EP2980405B1 - Distribution device for a hydraulic machine - Google Patents

Description

The present invention relates to a distribution casing device for a hydraulic machine comprising a casing part which has an open axial end and which has two main bores, respectively for the supply of fluid and for the escape of fluid, said bores opening in an inner axial face of the housing part, respectively by a first main orifice and a second main orifice which are successively arranged in the direction going axially away from the open axial end, the inner axial face presenting a first a second and a third internal sealing surface arrangement, respectively located between the open axial end and the first main port, between the two main ports and beyond the second main port with respect to the open axial end.

The hydraulic machine can be a hydraulic motor or a pump. Conventionally, the distribution housing device cooperates with an internal distributor which, itself, cooperates with a cylinder block. Thus, the internal distributor comprises distribution ducts which convey the supply or exhaust fluid to and from the cylinder block cylinder ducts. The internal distributor is disposed inside the distribution casing and has an outer axial face which cooperates with the internal axial face of the distribution casing device and a radial distribution face located towards the open axial end of this casing. The radial distribution face of the internal distributor rests against a communication face, also radial, of the cylinder block, such that the orifices of the distribution ducts located in the distribution face communicate alternately with the orifices of the cylinder ducts. located in the communication face of the cylinder block.

The internal distributor thus plays the role of interface between the main ports of the feed and exhaust bores which are in the internal axial face of the timing case and the communication face of the cylinder block. For this, the external axial face of the internal distributor has two main grooves, respectively in communication with each of the main holes of the inner axial face of the timing case, and the distribution ducts are connected either to one or to the another of these gorges.

The hydraulic machine can be of the type comprising a single active operating cylinder, in which case the structure of the internal distributor can be relatively simple, half of the distribution ducts being permanently connected to one of the main grooves, while the other half is permanently connected to the other groove and, if we consider the distribution face, the successive distribution ports belong to either, or to the other half.

However, the hydraulic machine may also be of the type having two operating displacements, in which case the internal distributor may be equipped with a displacement selector which, depending on its position, puts into communication certain distribution ducts or with one of the grooves. principal, with each other.

During the relative rotation between the cylinder block and the internal distributor, the orifices of the distribution ducts which are in the distribution face of the internal distributor are successively opposite a communication orifice of the cylinder block (for supply fluid or receive exhaust fluid from this orifice) and facing solid portions of the communication face. When the orifice of a distribution pipe is opposite a solid part, because of the fluid pressure prevailing in this orifice, a reaction force is produced against this solid part which tends to move the communication face away of the cylinder block of the distribution face of the internal distributor. However, for the fluid distribution to operate properly, it is important for the distribution face to bear against the communication face.

Thus, it is necessary to balance the forces by causing the aforesaid reaction forces, which tend to move the internal distributor of the cylinder block, to be compensated by opposing forces, tending to bring the internal distributor of the block- cylinders.

To create such a joining force, it is possible to use compression spring-type devices bearing on a bottom portion of the distribution casing opposite its open axial end and pushing the internal distributor towards this open axial end. In practice, such springs are effective only at the start of the hydraulic machine because it would be practically impossible to size them so that they can produce desired forces throughout the range of supply and exhaust pressure used during operation of the machine. For this reason, it is known to ensure that the approximation forces implement fluid pressures, which requires that the interface between the timing case and the distributor, particularly with respect to the main orifices of the internal axial face of the housing and the main grooves of the outer axial face of the distributor, has a suitable conformation to provide substantially radial bearing surfaces for the hydraulic fluid.

As indicated above, the internal fluid distributor may be of different types, in particular depending on whether the machine has one or two active operating displacements. Consequently, to allow the creation of the desired approximation forces by action of the fluid pressure at the interface between the internal distributor and the distribution casing, it is necessary that the internal axial face of the distribution casing is precisely adapted to the external axial face of the internal distributor.

In practice, this requires having as many types of timing case devices as there are types of internal fluid distributors. These constraints have a negative industrial impact since they require the design of a wide range of timing case devices without allowing the implementation of a common production tool and, therefore, without allowing large series.

The invention aims to remedy this drawback by proposing a distribution case device which is more easily usable for different types of internal fluid distributors, while offering the possibility of generating appropriate fluidic balancing forces.

This object is achieved by the fact that the first and second internal sealing surface arrangements are staggered internal arrangements, comprising two axial bearing surfaces stepped with respect to one another, separated by a shoulder facing towards the other. open axial end and that for each of the first and second stepped internal arrangements, only one of the axial bearing surfaces has an annular groove, adapted to receive a seal.

Thus, according to the assortment of the distribution case device with such or such type of internal distributor, the shoulders of stepped axial bearing surfaces are used or not to participate in hydraulic balancing.

Conventionally, when the machine is of the single-displacement type of operation, the hydraulic balancing can simply be effected by a conformation of the main distribution grooves of the internal distributor, adapted to those of the main orifices present in the inner axial face of the housing of distribution.

On the other hand, in the case of a machine with two displacement cylinders, that is to say a machine which comprises two sub-engines which, in full displacement, are both active while, in small displacement , only one of the sub-motors is active, the shoulders of the stepped axial bearing surfaces can be implemented to balance the hydraulic forces concerning the sub-motors that are not directly connected to the main ports, as it is will see in the sequel.

The presence of joints is required between the inner axial face of the housing portion and the outer axial face of the inner distributor to ensure a tight cooperation between these faces, limiting leakage outside the connection between the grooves and the orifices between which the fluid flows. Conventionally, the joints are arranged in the grooves that presents one or the other of these internal and external axial faces. It is interesting to provide some joints on the inner axial face of the housing part, waiting to receive a particular type of internal distributor.

In particular, if the internal distributor being adapted to a single-cylinder machine, the staged arrangements are not implemented for hydraulic balancing, the grooves present in the axial bearings of the stepped internal arrangements will be sufficient to ensure sealing, without having to additionally provide grooves with seals on the outer axial face of the dispenser.

On the other hand, if a groove is provided on only one of the axial bearing surfaces of each stepped arrangement and an internal two-cylinder displacement type distributor is used, requiring a seal on each of these axial bearings. , we will be able to provide that the internal distributor has a groove receiving a seal to cooperate with the axial bearing of the corresponding stepped internal arrangement which does not include a seal.

According to one option, the casing portion further has a secondary bore that opens into the inner axial face through a secondary port located beyond the second main port relative to the opening, and the third internal seal chamber arrangement. comprises two axial bearing surfaces located on the same diameter, on either side of the secondary orifice.

In this case, it can be provided that at least one of the axial bearing surfaces of the third internal sealing surface arrangement has an annular groove adapted to receive a seal.

As will be seen below, the secondary bore can in particular be used for controlling a displacement selector.

The seal provided on one of the axial bearing surfaces of the third internal sealing bearing arrangement serves to seal the connection between the housing portion and the inner distributor opposite the axial end. open the crankcase portion. Depending on the case, the secondary bore may be unused, in particular when the internal distributor is of the single-displacement type, a single seal on the third internal sealing bearing arrangement may then suffice. If, on the other hand, the secondary bore is used to convey fluid, it is then necessary to provide a seal cooperating with each of the two axial bearing surfaces of the third internal sealing surface arrangement. By producing this axial bearing surface on the same diameter, it is made to provide no fluid bearing surface disturbing the balancing by the fluid pressures. Thus, balancing is only achieved by the radial portions of the surfaces subjected to fluid pressures, i.e. by the conformations of the main orifices and main grooves, and those of the shoulders of the stepped axial bearing surfaces.

The invention also relates to a dispensing assembly for a hydraulic machine, which comprises a casing device according to the invention as set out above, possibly according to the various options mentioned above, as well as an internal distributor arranged in the part of a casing so that a radial face of distribution of the distributor is located towards the open axial end of the housing part and an external axial face of the distributor is facing the inner axial face of the housing part, said external axial face having a first and a second main groove respectively in view of the first and second main port, and a first, a second and a third arrangement of outer sealing surface, respectively adapted to cooperate with the first, the second and the third arrangement of internal sealing surface, the internal distributor comprising distribution ducts which open in the radial distribution face and are configured to be connected to one or other of the main grooves.

As previously indicated, depending on whether the internal distributor is of the single-cylinder or two-cylinder type, the balancing of the fluid pressures can be effected by the thrust of fluid exerted on the radial portions of the surfaces of the main grooves of the face. external axial internal distributor, or, in a complementary manner, on the shoulders of stepped internal arrangements provided on the inner axial face of the housing portion vis-à-vis corresponding shoulders located on the outer axial face of the distributor.

According to one option, each outer sealing span arrangement comprises a single axial span.

This is particularly the case when the internal distributor is of the single-cylinder type.

According to another option, at least one of the outer sealing surface arrangements is a stepped external arrangement, which is adapted to cooperate with one of the stepped internal arrangements and which comprises two stepped axial bearing surfaces, one for each relative to the other, separated by a shoulder turned on the opposite side to the distribution face; the distributor has an axial bore having a first, a second and a third selector orifice, which are successively arranged axially and which are respectively connected to a group of distribution ducts, one of the selector orifices being connected to the stepped external arrangement; and a select spool is movable in the bore between a first position in which the first and second selector ports are interconnected without being connected to the third selector port and a second position wherein the second and third selector ports are interconnected without being connected to the first selection port.

In this case, the internal fluid distributor is of the multi-displacement type of operation, the selection of the displacement being effected by the selection slide. The shoulders of the axial bearing surfaces of the staged arrangements are then used to achieve the desired balance.

It can be provided that the selection slide has a single selection groove which, in the first position of the slide, connects the first and second selector apertures and which, in the second position of the slide, connects the second and third selector apertures.

In this case, the conformation of the selection drawer is extremely simple.

According to yet another option, at least two of the external sealing surface arrangements are staggered external arrangements each adapted to cooperate with one of the stepped internal arrangements, each stepped external arrangement comprising two stepped axial bearing surfaces. one with respect to the other, separated by a shoulder turned on the opposite side to the distribution face; the distributor has an axial bore having a first, a second, a third and a fourth selection orifice, which are successively arranged axially and which are respectively connected, each, to a group of distribution ducts, two selection orifices of the four selector ports being respectively connected to one of the two stepped external arrangements; and a selection slide is movable in the bore between a first position in which the selection orifices are connected in pairs and a second position in which three of the selection orifices are connected between them, without being connected to the orifice remaining selection.

The internal distributor then also allows operation with two separate displacements, this time using four selection orifices.

In this case, it can be provided that the two selection orifices which are respectively connected to one of the two stepped external arrangements are two selection orifices which are not connected by the selection slide, in the first position of the latter.

It can also be provided that the selection slide comprises a connection which, in the second position of this slide, connects two selection orifices and a selector which, in this second position, connects said link with that of the two other orifices of selection which is at the lowest pressure, said remaining selection port thus being the one at the highest pressure.

The selection slide may have two selection grooves which, in the first position of the slide, respectively connect the first and second selection orifices, and the third and fourth selection orifices, whereas in the second position of the slide one said grooves connect the second and third selector ports.

• la figure 1 est une vue en coupe axiale d'une machine hydraulique avec un dispositif de carter de distribution selon l'invention, dans lequel est disposé un distributeur interne selon un premier type ;
• la figure 1A est une vue partielle prise de la figure 1, sur laquelle le dispositif de carter de distribution est agrandi ;
• la figure 2 montre le dispositif de carter de distribution selon l'invention, dans lequel est disposé un distributeur interne selon un deuxième type ;
• la figure 3 est une vue analogue à la figure 2, avec un distributeur interne d'un troisième type, en configuration de grande cylindrée ; et
• la figure 4 est une vue analogue à la figure 3, montrant la configuration de petite cylindrée.

The invention will be better understood and its advantages will appear better on reading the detailed description which follows, of an embodiment shown as non-limiting examples. The description refers to the accompanying drawings in which:

• the figure 1 is an axial sectional view of a hydraulic machine with a distribution case device according to the invention, in which is disposed an internal distributor according to a first type;
• the Figure 1A is a partial view taken from the figure 1 , on which the timing case device is enlarged;
• the figure 2 shows the distribution case device according to the invention, in which is disposed an internal distributor according to a second type;
• the figure 3 is a view similar to the figure 2 with an internal distributor of a third type, in a large displacement configuration; and
• the figure 4 is a view similar to the figure 3 , showing the configuration of small displacement.

We first describe the figure 1 which shows a hydraulic machine, in particular a hydraulic motor. However, it is understood that the invention also applies to other types of hydraulic machine, in particular a hydraulic pump.

In a manner known per se, the engine of the figure 1 comprises a housing 10 in three parts, respectively 10A, 10B and 10C. The first portion 10A of the housing is the timing case device. The second part 10B carries, on its inner periphery, a corrugated cam 2B. The third portion 10C serves in this case as a housing at the output shaft 12 of the hydraulic motor, maintaining this shaft in rotation by bearings 13. The output shaft cooperates, in particular by splines 14 or the like, with the inner periphery of a cylinder block 16 disposed in the portion 10B of the housing. Thus, the cylinder block 16 and the shaft 12 rotate together relative to the housing 10 about an axis of rotation A.

In a manner known per se, the cylinder block comprises a plurality of radial cylinders 18 in which pistons are arranged which cooperate with the cam 2B. The cylinder block comprises cylinder ducts 20 which communicate the cylinders 18 with the communication face 16A of the cylinder block.

The internal distributor 15, which is fixed in rotation with respect to the housing portion 10A, comprises distribution ducts whose openings open into a distribution face 15A of the internal distributor located at the open axial end 11A of the crankcase portion. 10A.

The distribution ducts are placed in communication with either a fluid supply or a fluid outlet. Their orifices which open into the distribution face 15A are organized with respect to the orifices of the roll ducts situated in the communication face of the cylinder block, so that, during the relative rotation of the cylinder block and the casing, the cylinder ducts are alternately placed in communication with the supply and with the exhaust.

On the figures 1 and 1A two distribution ducts are shown, respectively a first duct 22 connected to a first main groove 17 of the external axial face 15B of the distributor 15, and a second distribution duct 24 connected to a second main groove 19 of the external face 15B .

The housing portion 10A has two main holes, respectively 27 and 29, which communicate respectively with the grooves 17 and 19 above. More specifically, these holes open into the inner axial face 11B of the housing portion 10A, respectively by a first main port 27A and a second main port 29A. As seen, these two main ports are arranged successively in the direction S going away from the open end 11A of the housing portion 10A.

It is noted that, in this case, the housing portion 10A has a bell-shaped, with a bottom 11C opposite its open axial end 11A. It is in this case made in one piece, by foundry and / or machining. Of course, one could achieve the housing portion 10A in two parts, a first part open axially from one side, and a cover forming the bottom opposite the axial end open, attached to this first part.

It is noted that the internal axial face 11B has a first internal sealing surface arrangement 30, a second internal sealing surface arrangement 32, and a third internal sealing surface arrangement 34. The first arrangement 30 is located between the open axial end 11A and the first main port 27A, the second arrangement is located between the two main ports 27A and 29A, and the third arrangement is located beyond the second port 29A with respect to the open axial end.

Within the meaning of the present invention, an axial bearing surface area is a cylindrical surface of constant radius, oriented axially, which can cooperate sealing with a corresponding surface located vis-a-vis, via a seal. Within the meaning of the present invention, an internal sealing surface arrangement is an arrangement which comprises at least one internal axial sealing surface.

It will be seen that the first internal sealing surface arrangement comprises two axial bearing surfaces 30A and 30B, respectively, which are stepped with respect to each other, separated by a shoulder 30C which is turned towards the axial end. opened. Also, the second axial bearing arrangement comprises a first axial bearing surface 32A, a second axial bearing surface 32B which are staggered relative to each other, separated by a shoulder 32C which is also turned towards the open axial end 11A. In contrast, the third internal sealing surface arrangement comprises two axial sealing surfaces, respectively 34A and 34B, which are located on the same radius.

It can be seen that the bearing surface 30A of the first arrangement 30 has an annular groove 30D in which a seal 30 'is arranged, as well as the first axial bearing surface 32A. of the second arrangement 32 has an annular groove 32D in which is disposed a seal 32 '. In addition, in the example shown, the axial bearing surface 34B of the third arrangement 34 also comprises an annular groove 34C in which a seal 34 'is disposed.

We still notice on figures 1 and 1A that the housing portion 10A has a secondary bore 31 which opens into the inner axial face 11B of this housing portion through a secondary orifice 31A located beyond the second main port 29A in the direction away from the end axial open 11A. The two axial bearing surfaces 34A and 34B of the third internal bearing arrangement 34 are located on either side of this secondary opening 31A. However, in the example of figure 1 , using the internal distributor 15 which is shown, this secondary bore is unused, and it is in this case blocked by a plug 31B. One could also achieve the housing 10A without the secondary bore 31, is not machining it (its geometry is particularly simple) that when needed, as will be seen in connection with the figures 2 and 3 .

In the example of the figure 1 , the internal distributor 15 is simple, and it is also particularly light, being traversed from one side by a central bore 15 '. Its outer axial face 15B has three arrangements of external sealing surface. This is a first arrangement 40 located between the distribution face 15A and the first groove 17, a second arrangement 42 located between the grooves 17 and 19, and a third arrangement 44 located beyond the groove 19 with respect to the distribution face 15A. In this case, each of the outer seal arrangements 40, 42 and 44 includes a single axial span. These axial bearings cooperate simply with the seals 30 ', 32' and 34 'above, to establish a sealing contact between the face 11B of the housing 10A and the face 15B of the distributor, in several places, namely: between the face 11A and the first groove 17, between the two grooves 17 and 19, and beyond the second groove 19. In other words, this cooperation fluidly separates the two grooves 17 and 19 from one another and also separates them from the environment.

The distribution set represented on the figures 1 and 1A comprising the housing portion 10A and the internal distributor 15, is therefore particularly simple, used for a single displacement of operation, the internal distributor does not include displacement selector. To initially contact the distribution face of the distributor 15 with the communication face of the cylinder blocks, one or more springs 36 are arranged between the axial end of the internal distributor opposite its distribution face 15A and the bottom 11C of the part 10A of crankcase.

The seals 30 ', 32' and 34 'are respectively arranged in the grooves 30D, 32D and 34C and are arranged in these grooves before the introduction of the internal distributor 15 into the housing portion 10A, by an axial displacement of the distributor according to the arrow S of the Figure 1A . The external axial face 15B of the distributor has chamfers 30 ", 32" and 34 ", which cooperate respectively with the seals 30 ', 32' and 34 'during the insertion of the distributor into the housing part. may also be rounded portions such as holidays or the like, thus contribute to maintain the joints in place in their respective grooves during assembly of the dispenser.

We now describe the figure 2 , on which the housing portion 10A is identical to that of the figure 1 . However, the internal distributor 115 is different from the internal distributor 15. It has of course similarities with the latter, in particular two main grooves 117 and 119 which are located in its outer axial face 115B and are respectively opposite the first and second main port 27A and 29A of the housing portion 10A. It furthermore has a radial distribution face 115A bearing against the communication face 16A of the cylinder block. This internal distributor 115 comprises distribution ducts which open into the distribution face 115A and are configured to be connected to one or other of the main grooves 117 and 119. Furthermore, the external axial face 115B of the distributor internal 115 has three arrangements of external sealing surface, respectively 140, 142 and 144, which are respectively able to cooperate with the first, the second and the third arrangement of internal sealing surface 30, 32 and 34 of the part of housing 10A.

At least one of the external sealing bearing arrangements of the internal distributor, in this case the arrangement 142, is a stepped external arrangement which is adapted to cooperate with one of the internal arrangements. In this case, it is seen that this arrangement 142 comprises two axial bearing surfaces, respectively 142A and 142B which are staggered relative to one another by being separated by a shoulder 142C which is turned on the opposite side to the distribution face 115A. In other words, this shoulder 142C faces the shoulder 32C of the internal sealing bearing arrangement 32. The axial bearing surface 142A of the arrangement 142 co-operates with the axial bearing surface 32A of the arrangement 32 via the seal 32 '. Likewise, the axial bearing surface 142B cooperates with the axial bearing surface 32B of the arrangement 32 via a seal. In this case, this seal 142 'is disposed in a groove 142D made in the axial surface 142B. Thus, the space between the shoulders 32C and 142C opposite is sealed on both sides axially.

In contrast, the outer seal bearing arrangement 140 includes an axial bearing with a single axial surface, which cooperates with the surface 30A of the arrangement 30, via the seal 30 '. For its part, the external sealing surface arrangement 144 comprises a single axial bearing surface, with two axial surfaces 144A and 144B which respectively cooperate with the axial surfaces 34A and 34B, respectively via the gasket 34 'and via a gasket 144' located in a groove 144C of the axial surface 144A.

Unlike the case of figure 1 , the secondary bore 31 of the housing portion 10A is not plugged. It serves in fact to control a displacement slide 150 arranged in the internal distributor 115. For this, the end of the inner distributor 115 opposite its distribution face 115A has a control chamber 152 which is connected to the orifice secondary 31A via a hole 154 of the inner manifold 115. In this case, this hole 154 is arranged radially and communicates with the annular groove of the inner axial face of the housing portion 10A in which the secondary orifice 31A is located. In this case, the control chamber 152 is formed at the end of an internal central bore 153 of the distributor 115. This bore is oriented axially and the chamber 152 is disposed at the end of this bore which is opposite the distribution face 115A. The internal distributor 115 may be formed in a single block and, to simplify its manufacture, the conduit 154 may be a radial bore therethrough.

The axial bore 153 has a first, a second and a third selector orifice, 153A, 153B and 153C, respectively, which are arranged successively axially. In this case, these orifices are located in grooves of the bore, respectively 153'A, 153'B and 153'C. These orifices 153A, 153B and 153C are each respectively connected to a group of distribution ducts. We have shown on the figure 2 a conduit of each of these groups, namely a conduit 123A which communicates permanently with the orifice 153A, a conduit 123B which communicates permanently with the orifice 153B and a conduit 123C which communicates permanently with the orifice 153C. The orifice 153A is permanently connected to the main groove 119, so that the distribution ducts of the first group 123A communicate continuously with this groove and thus with the main bore 29. Similarly, the orifice 153C communicates with the groove 117, so that the distribution conduits of the third group 123C communicate permanently with the main orifice 27. In contrast, the orifice 153B is connected to the stepped external arrangement 142. It can be seen that via a section radial duct 123B '(there may be several) connected to a distribution duct of the second group 123B, the orifice 153B is connected to the space between the respective shoulders 32C and 142C arrangements 32 and 142. Thus, the fluid pressure circulating in the distribution ducts of the second group is supported on the shoulder 32C to act on the shoulder 142C and tend to push the distributor 115 to the communication face of the block-c ylindres, in the direction of arrow F.

In the position of the drawer 150 shown on the figure 2 , the outer annular groove 151 that presents this drawer, called selection groove, communicates the orifices 153B and 153C. As a result, the distribution conduits of the second group 123B are put under the same pressure as those of the third group 123C. This is the second position of the drawer, wherein the second and third selector ports 153B and 153C are interconnected without being connected to the first selection port 153A.

In the first position of the drawer, not shown, it is moved in the direction of the arrow S with respect to what the figure 2 , so that the throat 151 communicates with each other the first and second selection ports 153A and 153B, which are not then connected to the third selection port 153C.

For example, in a normal operating situation, the main port 29 serves for the supply of fluid, while the main port 27 serves for the escape of fluid. The number of distribution ducts of the third group is equal to the sum of the number of ducts of the first and second groups. When the drawer 150 is in its first position, all the distribution ducts of the first and second groups 123A and 123B are used for supply, while the distribution ducts of the third group 123C are used for the exhaust. The engine then operates in full displacement. On the other hand, in the second position of the drawer 150 shown on the figure 2 , only the distribution ducts of the first group 123A are used for the supply, while the distribution ducts of the second and third groups 123B and 123C are used for the exhaust. Thus, the sub-engine corresponding to the distribution ducts of the second group 123B and the subgroup of distribution channels 123C third group associated with it is inactivated, its distribution ducts being placed at the same pressure. As indicated above, via the communication of the hole 153B with the space between the shoulders 32C and 142C, the distributor is balanced.

In the non-preferential mode of operation, the main bore 29 serves the exhaust while the main bore 27 is used for feeding. In this case, in the second position of the selection slide 150 shown on the figure 2 , the distribution ducts of the second and third groups are placed at the same pressure which is then the supply pressure. The inactivated sub-motor is then subjected to the supply pressure, so that this sub-engine can oppose a resistant torque. This direction of operation in small displacement is then non-preferential.

It is the fluid pressure in the control chamber 152 which makes it possible to move the selection slide 150 towards its second position shown in FIG. figure 2 . This pressure is antagonistic to the return force exerted by a spring 155 disposed at the opposite end of the selector slide 150. This spring is supported, on the one hand, on the end 150A of the selection slide opposite the chamber 152 and on the other hand, on a cup 155 'secured to the body of the inner distributor 115, for example by means of a circlip or the like 156.

The body of the internal distributor 115 can be manufactured in one piece and, to complete this dispenser, it suffices to arrange the selection spool 150 in the bore 153, to set up the spring 155 and to fix the cup 155 '. The internal distributor 115 equipped with the selection drawer can then be handled as a whole.

In the example shown, only the axial end of the bore 153 located on the side of the open axial end 11A of the housing portion 10 is open, the opposite axial end being closed by a wall of a single block With the body of the dispenser 115. This wall could of course be reported and be fixed by any suitable means to the body of the dispenser.

Like that of figures 1 and 1A , the whole of the figure 2 comprises a spring 36 which cooperates with the housing portion 10A and with the internal distributor to move the latter from the bottom of the housing portion 10A opposite its open end. This makes it possible to initiate the support of the distribution face against the communication face, this support being reinforced, when the pressure increases while the engine is in operation, by the fluidic pressure produced by the fluid pressure in the grooves. 119 and 117. At the same time, the fluid pressure between the shoulders 32C and 142C contributes to this fluidic support with a suitable force, balancing the counter-support coming from the pressure of the fluid at the dispensing orifices against the solid parts of the communication face. Thus, whether the engine is operating in large displacement or in small displacement, the distribution face of the distributor is correctly applied against the communication face of the cylinder block, with the appropriate balancing.

We now describe the figures 3 and 4 , which show the application of the device of the invention to a motor with two active displacement cylinders. However, unlike that of the figure 2 this motor has no preferential direction of operation.

In these figures, the internal distributor 215 is disposed in the housing portion 10A which is identical to that of the figures 1 and 2 . The radial distribution face 215A of this distributor is located towards the open axial end 11A of the housing portion 10A and bears against the face communication 16A of the cylinder block. The external axial face 215B of the distributor is facing the inner axial face 11B of the housing portion 10A. This outer axial face 215B has two main grooves, respectively 217 and 219 respectively facing the first and second main orifices 27 and 29. It further has three external sealing surface arrangements 240, 242 and 244, respectively.

These arrangements of external sealing surface are respectively able to cooperate with the first, the second and the third arrangement of internal sealing surface 30, 32 and 34 of the housing portion 10A. The internal dispenser 215 includes dispensing ducts that open into the dispensing face 215A and are configured to be connected to one or other of the main grooves 217 and 219 via a select spool 250 movably mounted in a bore 253 axial distributor. Before describing the drawer in more detail, it will be noted that the two external sealing surface arrangements 240 and 242 are staggered arrangements. Indeed, they each have two axial bearing surfaces, respectively 240A, 240B and 242A, 242B which are staggered relative to each other by being separated by a shoulder, respectively 240C and 242C which is turned from the opposite side to the distribution face 215A. The outer bearing arrangements 240 and 242 which are staggered cooperate respectively with the arrangements of stepped internal bearing surface 30 and 32. Indeed, the shoulders 240C and 242C are respectively located opposite the shoulders 30C and 32C. On the other hand, the third external sealing surface arrangement 244 has two axial bearing surfaces 244A and 244B, respectively, which are located on the same diameter. These two axial surfaces cooperate respectively with the two axial surfaces 34A and 34B of the third external sealing surface arrangement.

Furthermore, the arrangement 240 has, on its axial surface 240B, a groove 240D in which is located a seal 240 ', just as the axial surface 242B has a groove 242D in which is located a seal 242'. Thus, the spaces between the shoulders 240C and 30C are sealed on both sides by the seals 30 'and 240', and the space between the shoulders 242C and 32C is sealed on both sides by the seals 32 'and 242'. The surface 244A axial has a groove 244C in which is located a seal 244 '. Thus, the orifice 31A of the secondary bore 31, which communicates with a bore 254 of the distributor 215, is sealed on both sides by the seals 244 'and 34'. The secondary bore thus serves to supply the control chamber 252 of the displacement selector located at the end of the selector slide 250 opposite the distribution face 215A.

The internal central axial bore 253 of the distributor 215 has four selector orifices, 253A, 253B, 253C and 253D respectively, which are successively arranged axially. These orifices open in annular grooves, respectively 253'A, 253'B, 253'C and 253'D. Each of the selection orifices is connected to a group of distribution ducts. It has thus been represented on the figure 3 a distribution duct 223A of the first group connected to the orifice 253A, a distribution duct 223B of the second group connected to the orifice 253B, a distribution duct 223C of the third group connected to the orifice 253C and a distribution duct 223D the fourth group connected to the port 253D. The selection port 253B is connected to the stepped external arrangement 242 via a conduit section 223B 'extending between the conduit 223B and the space between the shoulders 32C and 242C. Similarly, the selection port 253C is connected to the stepped external arrangement 240 via a conduit section 223C 'extending between the conduit 223C and the space between the shoulders 30C and 240C.

On the figure 3 , the drawer 250 occupies its first position, in which the selection orifices are connected in pairs. Indeed, the orifices 253A and 253B are interconnected by being isolated from the other two, while the orifices 253C and 253D are interconnected by being isolated from the other two. The selection orifice 253A is moreover permanently connected to the groove 219 and therefore to the main orifice 29, just as the selection orifice 253D is permanently connected to the groove 217 and therefore to the main orifice 27 Accordingly, in the first position shown on the figure 3 , the distribution ducts of the first and second groups 223A, 223B are all connected to the main port 29, while the distribution ducts of the third and fourth groups, 223C and 223D are all connected to the main port 27. More precisely the selection slide 250 has two selection grooves, 251A and 251B respectively, which in the first position of the slide shown in FIG. figure 3 , respectively connect the selection ports 253A and 253B, and the selection ports 253C and 253D. It is then a large displacement operation, the rotor of the motor rotating in a direction or in the opposite direction depending on whether the main orifices 27 and 29 respectively serve the supply and the exhaust or vice versa.

It is noted that the two selection orifices 253B and 253D which are respectively connected to the stepped arrangements 240 and 242 are not connected by the selection slide 250 in the first position of the latter illustrated on the drawing. figure 3 .

On the other hand, in the second position of the drawer 250 illustrated on the figure 4 the groove 251A connects the second and third selector ports 253B and 253C. In this situation, the selection groove 251B is only arranged opposite the third selection orifice 253D. The selector valve 250 moves from its first position to its second position by supplying fluid to the control chamber 252 via the secondary bore 31 and the bore 254 of the distributor 215. This fluid pressure has a counteracting effect on the force restoring force exerted by a spring 255 disposed at the opposite end of the selection slide 250. As in the example of the figure 2 this spring is supported, on the one hand, on the end 250A of the drawer 250 opposite the chamber 252 and, on the other hand, on a cup 255 'attached to the body of the distributor 215 via a circlip or the like 256.

The selection drawer comprises a link 260 which, in its second position illustrated on the figure 4 , interconnects the two selector ports 253B and 253C and a selector 262 which, in the second position of the spool 250, connects the link 260 with that of the two other selector orifices, 253A and 253D, which is at the lowest pressure . To simplify the drawings, link 260 and selector 262 are only shown on the drawing. figure 4 . This selector is represented in a very schematic way. It is a two-position and three-way valve, its output channel V1 being connected to the link 260 which is itself connected to the selection groove 251A so as to be connected to the orifices 253B and 253C when the drawer 250 is in its second position. The selector 262 comprises two input channels, respectively V2 and V3. In the example of the figure 4 , the channel V2 is connected to the groove 251B so as to be connected to the selection orifice 253D in the second position of the slide 250. The second input channel V3 of selector 262 is connected to an additional groove 251C of drawer 250 which, in the position shown in FIG. figure 4 , is facing with the orifice 253A. The lines 2 and 3, which respectively connect the channels V2 and V3 to the grooves 251B and 251C are also connected to respectively C2 and C3 control chambers. In the example shown, the pressure in the bore 29, which serves for the supply, is greater than the pressure in the bore 27 which serves for the exhaust. As a result, the pressure in the control chamber C3 is greater than the pressure in the control chamber C2, and the selector is placed in the position shown in FIG. figure 4 , in which it makes the channels V2 and V1 communicate, by isolating them from the channel V3. Thus, the link 260 is connected to the main port 27 at the lower pressure. It is understood that, if the pressure at the main orifice 27 becomes greater than the pressure at the main orifice 29, the selector moves to its second position, in which this time it communicates the channels V1 and V3, to place the connection 260 at the low pressure of the orifice 29.

In the situation of figure 4 , only the selection port 253A is connected to the high pressure of the main port 29, so that only the first group distribution conduits 223A are set to high pressure. On the other hand, the distribution ducts of the second and third groups, respectively 223B and 223C, are connected to the distribution ducts of the fourth group 223D via the link 260 and the selector 262, and are therefore put at the low pressure of the main orifice. Thus, the distribution ducts of the second and third groups 223B and 223C are placed at the same pressure, which is the exhaust pressure, and the corresponding sub-engine is deactivated. It is understood that if the pressure is reversed at the main orifices 27 and 29, it is this time the orifice 29 which serves for the exhaust and, by the selector 262, the link 260 is this time connected to the low pressure of the orifice 29, and the deactivated sub-motor, corresponding to the distribution ducts 223B and 223C is also put at the low pressure.

On the figures 3 and 4 , as in the previous figures, the spring 36 cooperates with the end of the distributor 215 opposite the distribution face 215A to make a first support between the distribution face and the communication face. Under the effect of the pressure of fluid in the distribution ducts, this first support is completed by a hydraulic support, performed by the fluid pressure exerted on the walls of the grooves 217 and 219, and also on the shoulders 242C and 240C opposite the shoulders 32C and 30C. Thus, even when the sub-motor corresponding to the distribution ducts of the second and third groups is deactivated, the hydraulic support is balanced.

Of course, the surfaces of the shoulders and grooves subjected to the pressure of hydraulic fluid to achieve the hydraulic support are dimensioned as a result of the support that is desired.

Thanks to the invention, with the same part of the distribution casing 10A, an engine is produced which can have a single displacement, or two displacements, according to two variants having either a preferred direction of operation, or no preferential direction of operation. In the case where this crankcase portion is used with an internal distributor to obtain two cubic capacity, and comprising a selection drawer 150 or 250, this drawer can be mounted in the body of the internal distributor being fixed in this body through to the cup 155 'or 255', so that the assembly thus obtained can be handled as a whole and placed in the housing part.

The wall of the internal distributor 215 opposite the dispensing face may be formed as a whole with the body of this dispenser, or may be attached to it, as for the internal distributor 115.

As in the embodiment of the Figure 1A , the external axial faces 115B and 215B of the distributors 115 and 215 of the Figures 2 to 4 have chamfers or the like, respectively 30 ", 32" and 34 "to cooperate respectively with the seals 30 ', 32' and 34 'during the insertion of the distributor in the housing part.

Likewise, the internal axial face 11B of the housing portion 10A has chamfers or the like (for example, fillets or rounded parts), respectively 42 "and 44", to respectively cooperate with the seals 142 '(or 2424) and 144 '(or 244') embodiments of the Figures 2 to 4 and help maintain these seals in their respective grooves, 142D (or 242D) and 144C (or 244C) when inserting the distributor into the housing portion.

Claims (16)

1. A distribution casing device for a hydraulic machine comprising a casing portion (10A) that has an open axial end (11A) and that has two main holes (27, 29), respectively for fluid feed and for fluid discharge, said holes opening out in an inside axial face (11B) of the casing portion (10A), respectively via a first main orifice (27A) and via a second main orifice (29A), which orifices are disposed in succession in the direction (S) going axially away from the open axial end (11A), the inside axial face having first, second, and third sealing inside bearing surface arrangements (30, 32, 34), respectively situated between the open axial end (11A) and the first main orifice (27A), between the two main orifices (27A, 29A), and beyond the second main orifice (29A) relative to the open axial end (11A),
   characterized in that the first and second sealing inside bearing surface arrangements are staggered inside arrangements (30; 32), comprising two axial bearing surfaces (30A, 30B; 32A, 32B) that are staggered relative to each other, and that are separated by a shoulder (30C; 32C) facing towards the open axial end and in that, for each of the first and second staggered inside arrangements (30; 32), only one (30A, 32A) of the axial bearing surfaces has an annular groove (30D, 32D), suitable for receiving a sealing gasket (30', 32').
2. The device according to claim 1, characterized in that the casing portion is further provided with a secondary hole (31) that opens out in the inside axial face (11B) via a secondary orifice (31A) situated beyond the second main orifice relative to the open axial end (11A) and in that the third sealing inside bearing surface arrangement (34) has two axial bearing surfaces (34A, 34B) situated at a same diameter on either side of the secondary orifice (31A).
3. The device according to claim 2, characterized in that at least one of the axial bearing surfaces (34B) of the third sealing inside bearing surface arrangement (34) has an annular groove (34C), suitable for receiving a sealing gasket (34').
4. A distribution assembly for a hydraulic machine, characterized in that it comprises a distribution casing device according to any one of claims 1 to 3, and an internal distributor (15; 115; 215), arranged in the casing portion (10A) in such a manner that a radial distribution face (15A; 115A; 215A) of the distributor is situated in the vicinity of the open axial end (11A) of the casing portion (10A) and that an outside axial face (15B ; 115B ; 215B) of the distributor faces the inside axial face (11B) of the casing portion (10A), said outside axial face having first and second main grooves (17, 19 ; 117, 119 ; 217, 219) facing respective ones of the first and second main orifices (27A, 29A), and first, second, and third sealing outside bearing surface arrangements (40, 42, 44 ; 140, 142, 144 ; 240, 242, 244), suitable for co-operating with respective ones of the first, second, and third sealing inside bearing surface arrangements (30, 32, 34), the internal distributor (15; 115; 215) having distribution ducts (22, 24; 123A, 123B, 123C; 223A, 223B, 223C, 223D) that open out in the radial distribution face (15A; 115A; 215A) and that are configured to be connected to one or the other of the main grooves (17, 19 ; 117, 119 ; 217, 219).
5. The assembly according to claim 4, characterized in that each sealing outside bearing surface arrangement (40, 42, 44) comprises a single axial bearing surface.
6. The assembly according to claim 4 or 5, characterized in that the internal distributor (15) has no displacement selector and is thus intended to be used for a single operating displacement, and in that the outside axial face of the internal distributor is devoid of grooves for receiving sealing gaskets.
7. The assembly according to claim 4, characterized in that at least one of the sealing outside bearing surface arrangements (142) is a staggered outside arrangement that is suitable for co-operating with one of the staggered inside arrangements and that comprises two staggered axial bearing surfaces (142A, 142B) that are staggered relative to each other and that are separated by a shoulder (142C) facing in a direction opposite from a direction in which the distribution face (115A) faces, in that the distributor (115) has an axial bore (153) having first, second, and third selection orifices (153A, 153B, 153C), that are disposed in axial succession, each one of said selection orifices being connected to a group of distribution ducts (123A, 123B, 123C), one of the selection orifices (153C) being connected to the staggered outside arrangement, and in that a selection slide (150) is mounted to move in the bore (153) between a first position in which the first and second selection orifices (153A, 153B) are interconnected without being connected to the third selection orifice (153C), and a second position in which the second and third selection orifices (153B, 153C) are interconnected without being connected to the first selection orifice (153A).
8. The assembly according to claim 7, characterized in that the internal distributor is provided with a displacement selector, and is of the two operating displacement type requiring a sealing on each of the axial bearing surfaces of the staggered arrangements, and in that one of the axial bearing surfaces (142B) of the staggered outside arrangement (142) has a groove (142D) receiving a sealing gasket (142') for co-operating with that (32B) of the axial bearing surfaces of the corresponding staggered inside arrangement (32) that does not have a sealing gasket.
9. The assembly according to claim 7 or 8, characterized in that the selection slide (150) has a single selection groove (151) that, when the slide (150) is in the first position, interconnects the first and second selection orifices (153A, 153B) and that, when the slide is in the second position, interconnects the second and third selection orifices (153B, 153C).
10. The assembly according to claim 4, characterized in that at least two of the sealing outside bearing surface arrangements are staggered outside arrangements (240, 242), each of which is suitable for co-operating with a respective one of the staggered inside arrangements, each staggered outside arrangement comprising two axial bearing surfaces (240A, 240B, 242A, 242B) that are staggered relative to each other and that are separated by a shoulder (240C, 242C) facing in a direction opposite from a direction in which the distribution face (215A) faces, in that the distributor has an axial bore (253) that has first, second, third, and fourth selection orifices (253A, 253B, 253C, 253D) that are disposed in axial succession, each one of said selection orifices being connected to a respective group of distribution ducts (223A, 223B, 223C, 223D), two selection orifices (253B, 253D) from among the four selection orifices being connected to respective ones of the two staggered outside arrangements (240, 242), and in that a selection slide (250) is mounted to move in the bore between a first position in which the selection orifices are interconnected in pairs and a second position in which three of the selection orifices (253A, 253C, 253D) are interconnected, without being connected to the remaining selection orifice (253A).
11. The assembly according to claim 10, characterized in that the internal distributor is provided with a displacement selector, and is of the two operating displacement type requiring a sealing on each of the axial bearing surfaces of the staggered arrangements, and in that one of the axial bearing surfaces (240B, 242B) of each of the staggered outside arrangements (240, 242) has a groove (242D, 242D) receiving a sealing gasket (240', 242') for co-operating with that of the axial bearing surfaces of the corresponding staggered inside arrangement that does not have a sealing gasket.
12. The assembly according to claim 10 or 11, characterized in that the two selection orifices (253B, 253D), which are connected to respective ones of the two staggered outside arrangements (240, 242), are two selection orifices that are not interconnected via the selection slide (250), when said slide is in its first position.
13. The assembly according to any one of claims 10 to 12, characterized in that the selection slide (250) includes a link (260) that, when the slide is in the second position, interconnects two selection orifices (253B, 253C), and a selector (262) that, when the slide is in said second position, connects said link to that one of the other two selection orifices (253A, 253D) that is at the lower pressure, the remaining one of said selection orifices thus being the one that is at the higher pressure.
14. The assembly according to any one of claims 10 to 13, characterized in that the selection slide (250) has two selection grooves (251A, 251B) that, when the slide is in the first position, respectively interconnect the first and second selection orifices (253A, 253B), and the third and fourth selection orifices (253C, 253D), whereas, when the slide is in the second position, one of said grooves interconnects the second and third selection orifices (253B, 253C).
15. The assembly according to any one of claims 7 to 14, characterized in that the casing device is according to claim 2 and in that the secondary orifice (31A) is connected to a control chamber (152; 252) of the selection slide (150; 250).
16. The assembly according to any one of claims 4 to 15, characterized in that it includes at least one spring (36) co-operating with the casing device (10A) and with the internal distributor (15 ; 115 ; 215) to move said internal distributor away from that end wall of the casing portion that is opposite from said open axial end.

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